Antifriction bearing



April 3, 1934. I I P. BRUHL 1,953,550

ANTIFRICTION BEARING 1 Filed June 20, 1932 ANTIFRICTION BEARING Paul Briihl, Berlin-Lichtenberg, Germany, as-

signor to Max Staub, Calcutta, British India Application June 20, 1932, Serial No. 618,339 In Germany .inne 20, 1931 My invention relates to antiiriction bearings, ing a divided outer race as described, the two and more particularly to bearings with inn-er and par s ar Co cte y preferably annular C011- outer race members, and a plurality of race ways necting members which are distributed over the between them. Antifriction members are arperimeter of the outer race and possess a limited ranged in a row in each raceway, and antifricde ee O resi y.

tion spacing members arranged intermediate the y th se nc S t hardened and ground inner antifriction members in each two adjacent raceface of the outer race is conserved in its prop r ways. a shape as required for a precision bearing, not- It is an object of my invention to improve a withstanding the resilient connection of the two bearing of this general type. parts. 65

To this end, I provide means for forcing radial- If in a bearing hav a divided er a s ly inwards the spacing members which in turn described, excessive stress is exerted on the races force the antifriction members in the raceways by the antifriction means, the stress will be abaway from each other and eliminate their slack sorbed without dama '6 the bearing 215 under in the race-ways. an axial thrust exceeding the normal force, the 7G By way of example, I shall illustrate and de parts of the outer race move apart slightly against scribe ball bearings with double raceways but it the reaction or their resilient connecting memis understood that I am not limited to ball bearbers. ings and not to any definite number of raceways. The resilient connec i g members y be 20 By designing an antifriction bearing according ified in various ways and are preferably dis- 75 to my invention, the elimination of slack renders tributed over, and sunk in, the outer perimeter it particularly suitable for very heavy loads and of the outer race. very high speeds, and the bearing runs very In the accompanying drawing, two types of smoothly. ball bearings embodying my invention are illus- Bearings designed according to my invention trated by way of example. 80

are equally suitable for push fit and for force fit In the drawing on their shafts, and the operation of the bearing Fig. 1 is an axial section, is not influenced by the character of the fit. In Fig. 2 is an elevation, with the outer race and conformity with the more or less tight fit, the the cage for the spacing antifriction members antifriction members are forced more or less topartly broken away, of the first type, and s5 ward the central plane of the bearing when the Fig. 3 is an axial section of the second type. bearing is fitted on the shaft. This is due to the Referring now to the drawing, a is the inner fact that the means for forcing radially inwards race member and b, b are the parts of the outer the spacing members, normally a cage, is more race member which is divided on the central or less expanded and its reaction more or less inplane of the hearing. The balls in the raceway 90 T creased. In this manner the antifriction memat b are c, and the balls in the raceway at b ers in the raceways are automatically adjusted are 0.

into the proper position between the races, and By way of example, cageless ball bearings are the good running condition of the bearing is conshown which have the advantage that there are served even under very heavy force fits. more balls per raceway than in a bearing having 95 Obviously the displacements and deformations a cage, and the bearing capacity of the bearing referred to are quite small. is high.

0 go running and high bearing paci y O h are spacing balls, of known type, which are b a rding to my i ve ti n the d ameter inserted between the rows of balls in the raceof the antifriction means in the raceways should ways and are much smaller than these balls, 166

be of the order of 1.6 times the diameter of the preferably at the rate oil by 1,6, as mentioned, spa i members- 2' is the cage of the spacing balls h which is cen- It is another object y inVentiOn to o tered in any suitable manner so that it is not dissign a bearing of the type e e t that it placed radially to any appreciable extent when the will yield to shocks and the excessive stress rebearing rotates. The balls 0, c are pitched very 165 sult therefrom. near together axially and the separating or spac- To this end, I divide the outer race member ing balls h may even be so arranged that the and provide resilient means for holding its parts balls 0, c are in contact. The cage 2' for the engaged with each other. spacing balls h is comparatively thin and its in- A i In a preferred embodiment of a bearing havside diameter is so determined that it bears on the spacing balls h with a certain tension, forcing the spacing balls in between the balls 0, 0' so that the latter are moved apart and are applied to their raceways without clearance.

is are the connecting members for the two parts of the divided outer race member b, b which may be split or closed and slightly resilient rings in grooves Z in the outer perimeter of the outer race member, preferably circular, with semicircular cores m, m for the inner faces of rings is to bear on. The rings are distributed over the perimeter of the outer race member. For instance, there may be three rings which are preferably pitched at unequal respective distances so that the two parts of the outer race member can be assembled only in a definite relative position.

Referring now particularly to the first type illustrated in Figs. 1 and 2, the balls 0 bear on the inner race member a at e, and on the outer race member part b at d, and e, d are the corresponding points for the balls c. Tangents to the raceways in the points where the balls bear on the raceways, are substantially parallel, as shown at f, g for the points d, e and at g for the points at, e. The angle the pairs of parallel tangents include with the axis of the bearing, is quite small.

If the bearing in Figs. 1 and 2 is placed on a shaft at force fit, the balls 0, c are forced slightly inward by the inner race member a and now bear on their respective raceways in such manner that the tangents are at a somewhat more acute angle than in the bearing in its unfitted condition, as shown in Fig. 1. The tension of the cage 1' is increased to some extent as the spacing balls h are forced radially outwards by the balls 0, 0'.

Referring now to Fig. 3, in this type the tangents f, g and f, 9 form cones, with their apices at o and 0', respectively, on the axis of the bearing. In this type, resultant forces act on the balls 0 and c in the direction of the arrows n and n, respectively which tend to move inwards the balls 0, c. The extensions of the arrows n and n go through the points 0 and 0', respectively. The forces in the direction of arrows n, n are absorbed by the spacing balls h on which cage 2' exerts a certain reaction.

In both types owing to the fact that the parts I), b of the outer race are resiliently connected by the rings is they can move apart for a slight amount when the axial thrust exerted by the balls (2, c exceeds a certain limit, the amount being only a few hundredths of a millimetre, but this is enough for reducing to a minimum the action of a shock on the bearing. When the excessive stress ceases, the parts of the outer race return into their initial position by the reaction of rings is in which the end faces of the two parts 2), b make a perfectly tight fit.

I claim:

1. A multiple row ball bearing with suitable race members having race-ways, comprising rows of bearing balls and spacing balls arranged between the rows of bearing balls, said spacing balls being adapted to rotate with the rows of bearing balls, a guide ring surrounding said spacing balls, said guide ring forcing the spacing balls radially inwards with such a tension that the bearing balls are forced positively laterally outward to such an extent that they lie absolutely without clearance between the two bearing race members.

2. A multiple row ball bearing according to claim 1, in which, in the case of a not built-in bearing, the tangents at the contact points of each bearing ball lie with their two inclined racev/ays substantially parallel, the race-ways being curved in such a manner that the bearing balls are forced by the inner race member toward the center of the bearing with the inner race member positioned on the shaft and the race-Ways come in contact so that the tangents at the contact points enclose a more acute angle than heretofore while at the same time the tension of the guide ring for the spacing balls become greater than heretofore.

3. A multiple row ball bearing according to claim 1, with at least one race member divided transversely to the ax s of the bearing into two parts, resilient split rings adapted to hold the two parts of said race member together, said rings having slight resiliency, and being distributed over the periphery of the race member and countersunk therein so as not to project beyond the peripheral surface.

PAUL Bath-1L. 

